ES2361088T3 - HEAT EXCHANGE AND AIR CONDITIONER. - Google Patents

Abstract

In a heat exchanger for exchanging heat between fluid such as refrigerant and air, an object of the present invention is to extend the surface area of fins while suppressing an increase in ventilation resistance, thereby improving performances of the heat exchanger. Corrugated sheet fins (70) are provided as the fins of the heat exchanger (60). The corrugated sheet fins (70) are each shaped like a corrugated sheet. The ridgeline direction of the waveform of the corrugated sheet fins (70) is orthogonal to front edges and rear edges. In the heat exchanger (60), the plurality of corrugated sheet fins (70) are arranged at constant pitches in the axial direction of the heat transfer tube (61).

Description

Technical field

The present invention relates to a heat exchanger and an air conditioner with the heat exchanger.

Background Technique

Traditionally, a heat exchanger for exchanging heat between a fluid, such as a refrigerant and air, has been known and widely used in air conditioners and similar devices. As the heat exchanger itself, as disclosed in JP-A-2001-304783, for example, a heat exchanger is known in which a multiplicity of fins in the form of flat sheets are arranged along a heat transfer tube at predetermined steps. In this type of heat exchanger, a fluid, such as a refrigerant, flows through the heat transfer tube while the air passes between the fins arranged at the predetermined passages, thereby exchanging heat between the fluid and the air.

Document JP-A-03-030062 discloses a heat exchanger incorporating fins that take the form of flat sheets only.

JP-A-2004-162885 discloses a solids filling tank where a heat exchanger is housed. The heat exchanger comprises a heat transfer tube and a plurality of fins arranged in axial direction with respect to the heat transfer tube and is configured to exchange heat between the fluid flowing through the heat transfer tube and the solid particles located inside the solids filling tank. The fins consist of a plurality of flat sheet fins and a plurality of corrugated sheet fins, which are alternately arranged in the axial direction with respect to the heat transfer tube. This configuration has been chosen in order to restrict the displacement of solid particles located inside the tank so that they do not move in a downward direction. The heat exchanger of this document is especially used in a fuel installation of a vehicle with hydrogen fuel cells

JP-A-08-0009444 also discloses a heat exchanger that incorporates only a plurality of flat blade fins.

Document GB-A-1 576 441 and document US-A-1,913,742 disclose a heat exchanger incorporating the distinctive features defined in the preamble of claim 1.

Disclosure of the invention

Problems that the invention must solve

In general, to improve the performance of the heat exchanger, a method for extending the surface area of the fins, that is, the area of heat transfer on the air side, is effective. On the other hand, in the heat exchanger mentioned above, which uses the flat-blade fins and the heat transfer tube, to increase the surface area of the fins, the passages between the fins need to be shortened. However, in this type of heat exchanger, when the passages between the fins become shorter, an area narrows where the air passes and the resistance to ventilation increases. For this reason, there is a limit on the improved performance of the heat exchanger to shorten the passages between the fins.

In consideration of these circumstances, an objective of the present invention is to extend to the surface area of the fins while suppressing an increase in the ventilation resistance of a heat exchanger to exchange heat between a fluid, such as a refrigerant, and air, thus improving the performance of the heat exchanger. Another object of the present invention is to provide an air conditioner using said high performance heat exchanger.

Means to solve the problems

The invention proposes a heat exchanger that offers the distinctive features of claims 1 or

2.

Each corrugated sheet fin 70 may be in contact with the flat sheet fins 65 located on both sides of the corrugated sheet fin 70.

The flat portions 78 may be formed along the sides of the corrugated sheet fins 70 orthogonal to the direction of the crest line of the waveform of the fins.

Adsorption layers made of adsorbent may be formed on the fins and moisture is transferred between the air passing between the fins and the adsorption layers.

The adsorption layers made of adsorbent may be formed on the surfaces of either flat sheet fins 65 or corrugated sheet fins 70, and moisture is transferred between the air that passes between flat sheet fins 65 and the corrugated sheet fins 70 and the adsorption layers.

Air conditioners incorporating a heat exchanger such as the one described above, are described in claims 7 to 9.

Functioning

According to the invention, the flaps of the flat sheet 65 and the flaps of corrugated sheet 70 are arranged to form the fins. In the heat exchanger 60, the flaps of flat sheet 65 and the flaps of corrugated sheet 70 are arranged so alternated in the axial direction of the heat transfer tube 61. In the heat exchanger 60, air passes between the corrugated sheet fins 70 from the front surface to the rear surface of the heat exchanger 60. In the sheet fins corrugated 70, the direction of the amplitude of the waveform is substantially parallel to the axial direction of the heat transfer tube 61. In the corrugated sheet fins 70, the direction of the crest line of the waveform is substantially orthogonal to the front surface and the rear surface of the heat exchanger 60. That is, the direction of the crest line of the waveform of the sheet fins cor rumpled 70 substantially corresponds to the direction of air passage in heat exchanger 60. Corrugated sheet fins 70 are each shaped as a corrugated sheet and, therefore, have a surface area greater than the fins shaped like a flat sheet of the same size. When the corrugated sheet fins 70 are arranged in the heat exchanger 60 to constitute the aetas, an area of heat transfer with the air can be increased without causing the passage between the fins to be smaller.

According to one aspect of the invention, each corrugated sheet fin 70 is in contact with the flat sheet fins 65 located on both sides of the corrugated sheet fins 70. That is, the upper portions of the waveform of the Corrugated sheet fin 70 is in contact with one of the adjacent flat sheet fins 65. The lower portions of the waveform of the corrugated sheet fin 70 is in contact with the other of the adjacent flat sheet fins 65.

According to another aspect of the invention, through holes 66, 75 are formed on the flaps of flat sheet 65 and on the fins of corrugated sheet 70, respectively. In the heat exchanger 60, heat transfer tubes 61 are inserted into the through holes 66, 75 of the flat blade fins 65 and the corrugated sheet fins 70, causing the situation in which the heat transfer tubes Heat transfer 61 passes through the flat blade fins 65 and the corrugated sheet fin 70.

According to the invention, the first collars 67 are formed on the flaps of flat sheet 65 and the second collars 76 are shaped on the fins of corrugated sheet 70. In each flat blade fin 65, the first collar 67 is constituted so that be cylindrical and in continuity with the periphery of the through hole

66. In each corrugated sheet flap 70, the second collar 76 is constituted to be cylindrical and in continuity with the periphery of the passage hole 75.

In accordance with one aspect of the invention, the first collars 67 of the flat-blade fins 65 are inserted into the second collars 76 of the corrugated sheet fins 70 and the heat transfer tubes 61 are inserted into the first collars 67 of the flaps of flat sheet 65. In the heat exchanger 60, placing the inner circumferential surfaces of the first collars 67 in intimate contact with the inner circumferential surfaces of the heat transfer tubes 61, the flaps of flat blade 65 they are fixed to the heat transfer tubes 61. In the heat exchanger 60, by placing the inner circumferential surfaces of the second collars 76 in intimate contact with the outer circumferential surfaces of the first collars 67, the corrugated sheet fins 70 are fixed to flat blade fins 65.

According to another aspect of the invention, the second collars 76 of the corrugated sheet fins 70 are inserted into the first collars 67 of the flat sheet fins 65 and the heat transfer tubes 61 are inserted into the second collars. 76 of the corrugated sheet fins 70. In the heat exchanger 60, placing the inner circumferential surfaces of the second collars 76 in intimate contact with the outer circumferential surfaces of the heat transfer tubes 61, the corrugated sheet fins 70 are fixed to the outer circumferential surfaces of the heat transfer tubes 61. In the heat exchanger 60, placing the inner circumferential surfaces of the second collars 76 in intimate contact with the outer circumferential surfaces of the first collars 67, the blade fins Corrugated 70 are fixed to the flaps of flat sheet 65.

According to one aspect of the invention, the flat portions 78 are formed on the corrugated sheet fins 70. On the corrugated sheet fins 70, the flat portions 78 are shaped along sides of the corrugated sheet fin 70 , which are orthogonal to the direction of the crest line of the waveform of said fins. In the corrugated sheet fins 70, the flat portion 78 may be formed along one of the two orthogonal sides with respect to the direction of the crest line of the waveform of said fins or they may be shaped along on both sides orthogonal with respect to the direction of the crest line of the waveform of said fins.

According to another aspect of the invention, the adsorption layers are formed on the fin surfaces. That is, when the heat exchanger 60 is provided with the corrugated sheet fins 70, the adsorption layers are formed on the surfaces of the corrugated sheet fin 70. When the heat exchanger 60 is provided with both flat sheet fins 65 like corrugated sheet fins 70, the adsorption layers are formed on the surfaces of flat sheet 65 and on the surfaces of the corrugated sheet fins 70. In the heat exchanger 60 according to the present aspect of the invention, the air that passes between the fins is in contact with the adsorption layers and moisture is transferred between the air and the adsorption layers. For example, when a heating means for cooling is supplied to the heat transfer tubes 61, the adsorption of moisture from the air in the adsorption layers is accelerated. When a heating means for heating is supplied to the heat transfer tubes 61, the desorption of moisture from the moisture layers is accelerated.

According to a further aspect of the invention, in the heat exchanger 60 provided with both flat sheet fins 65 and corrugated sheet fins 70, the adsorption layers are formed on the surfaces of either flat sheet fins 65 or of the corrugated sheet fins 70. In the heat exchanger 60 according to this aspect of the invention, the air passing between the flat sheet fins 65 and the corrugated sheet fins 70 is placed in contact with the layers of adsorption and moisture is transferred between the air and the adsorption layers. For example, when the heating means for cooling is supplied to the heat transfer tubes 61, the adsorption of the moisture from the air of the adsorption layers is accelerated. When the heating medium for heating is supplied to the heat transfer tubes 61, the desorption of moisture through the adsorption layers is accelerated.

According to another aspect of the invention, the temperature control part 55 and the humidity control parts 56, 57 are arranged in the air conditioner 10. The temperature control part 55 processes the heat load sensitive interior for adjusting the temperature of the air supplied to the interior space. The humidity control parts 56, 57 process the internal latent heat load to adjust the humidity of the air supplied to the interior space. The air conditioner 10 performs at least one heating and dehumidification operation. During the cooling and dehumidification operation, the temperature control part 55 cools the air supplied to the interior space and the humidity control parts 56, 57 dehumidify the air supplied to the interior space.

The temperature control part 55 according to this aspect of the invention is constituted by the temperature control heat exchanger 55 constituted by the heat exchanger 60, in accordance with what has been previously described. That is, the temperature control heat exchanger 55 is constituted by the heat exchanger 60 provided with the corrugated sheet fins 70. During the cooling and dehumidifying operation of the air conditioner 10, the heating means for cooling is supplied to the heat transfer tubes 61 of the temperature control heat exchanger 55, thereby cooling the air passing through the temperature heat exchanger 55. On the other hand, humidity control parts 56, 57 adjust the water content of the air by using the adsorbent. During the cooling and dehumidifying operation of the air conditioner 10, the humidity control parts 56, 57 allow the air supplied to the interior space to be in contact with the adsorbent, thereby adsorbing the moisture contained in the air by the adsorbent

Here, when the heating means is supplied, for cooling, to the heat transfer tubes 61 of the heat exchanger 60, the air humidity can condense on the fin surfaces. In this case, it is necessary to process the condensed water (drainage water) generated on the fin surfaces. On the contrary, in the heat exchanger 60, according to an aspect of the invention, since the air humidity is adsorbed by the adsorption layers located on the fin surfaces, even when the heating means is supplied, to cool, to the heat transfer tubes 61, the drain water is barely generated or not generated at all on the fin surfaces. In the air conditioner 10 according to this aspect of the invention, since the temperature control parts 56, 57 process the latent heat load by adjusting the air temperature, the temperature control part 55 You only need to process the sensible heat load. Accordingly, in the temperature control heat exchanger 55 which constitutes the temperature control part 55, even when the heating means is supplied to cool, to the heat transfer tubes 61, the water Drainage is hardly generated or not generated at all on the surface of the fins. The heat exchanger 60 incorporating the corrugated sheet fins 70 in accordance with the mentioned aspects of the invention is indicated for applications that do not require such drainage water processing.

In accordance with other aspects of the invention, the heat exchanger incorporating the adsorption layers and the circuit 40 of the heating medium connected to the heat transfer tube 61 of the heat exchanger are arranged in the air conditioner 10. The conditioner of air 10 alternately carries out the movement of supply of the heating means, to cool towards the heat transfer tube 61 of the

5

fifteen

25

35

Four. Five

heat exchanger and the supply movement of the heating means for heating towards the heat transfer tube 61 of the heat exchanger. When the heating medium is supplied, to cool, to the heat transfer tubes 61 of the heat exchanger, the adsorption of moisture from the air in the adsorption layers is accelerated. When the heating medium is supplied, to heat the heat transfer tubes 61, moisture desorption of the adsorption layers is accelerated. The air conditioner 10 discharges either the dehumidified air by taking the moisture through the heat exchanger adsorption layers and the humidified air receiving the moisture desorbed by the heat exchanger adsorption layers to condition the indoor air.

Effects of the invention

In accordance with the present invention, the corrugated sheet fins 70 formed as a corrugated sheet are arranged in the heat exchanger 60 to constitute the fins. For this reason, by using corrugated sheet fins 70, each with a surface area greater than a surface area of a flat sheet fin, a heat transfer area with air in the heat exchanger Heat 60 can be extended without causing the passage between the fins to be smaller. In the heat exchanger 60 according to the present invention, since the direction of the crest line of the waveform of the corrugated sheet fins 70 is substantially orthogonal to the front surface and the rear surface of the heat exchanger 60 , the flow of air passing through the heat exchanger 60 is hardly obstructed by the fins of corrugated sheet 70. Accordingly, according to the present invention, the area of heat transfer with the air can be extended by suppressing while increasing the ventilation resistance of the heat exchanger 60 and, thus, the performance of the heat exchanger 60 can be greatly improved compared to the traditional technique.

In particular, according to aspects of the invention, the flat portions 78 are formed along the sides of the corrugated sheet fins 70. The flat portions 78 make it possible to ensure the rigidity of the corrugated sheet fins 70. Accordingly, According to the present invention, the deformation of the corrugated sheet fins 70 can be avoided without causing the thickness of the corrugated sheet fins 70 to be greater.

By forming the adsorption layers on the fin surfaces, the heat exchanger 60 has the function of adsorbing and desorbing the humidity of the air. According to one aspect of the invention, since the heat exchanger 60 is provided with corrugated sheet fins 70, a sufficient area of the adsorption layers can be ensured. Accordingly, in accordance with this aspect of the invention, the moisture adsorption and desorption capacity of the heat exchanger 60 with the adsorption layers can be improved.

In accordance with other aspects of the invention, the heat exchanger 60 set forth above, is used as a temperature control heat exchanger 55 to mainly process the sensible heat load, that is, in accordance with these aspects of the present invention, since the high-performance heat exchanger 60 incorporating the corrugated sheet fins 70 of the invention is used as a temperature control heat exchanger 55 that does not require drainage water processing, the air conditioner 10 It can be reduced in size while ensuring the performance of the air conditioner 10.

According to aspects of the invention, the humidity of the air is adjusted by using the heat exchanger 60 set forth above. This is, in accordance with the present invention, since the high-performance heat exchanger 60 incorporating the corrugated sheet fin 70 according to the invention, the air conditioner 10 can be reduced in size while ensuring the ability to adjust of the humidity of the air conditioner 10.

Brief description of the drawings

Fig. 1 is a view of a schematic configuration showing the configuration of an air conditioner according to a first embodiment;

Fig. 2 is a view of a schematic configuration showing a first movement during a cooling and dehumidifying operation of the air conditioner according to the first embodiment;

Fig. 3 is a view of a schematic configuration showing a second movement during the cooling and dehumidification operation of the air conditioner according to the first embodiment;

Fig. 4 is a view of a schematic configuration showing a first movement during a heating and humidifying operation of the air conditioner according to the first embodiment;

Fig. 5 is a view of a schematic configuration showing a second movement during a heating and humidifying operation of the air conditioner according to the first embodiment;

Fig. 6 is a view of a schematic configuration showing a configuration of a refrigerant circuit and movements during the cooling and dehumidification operation according to the first embodiment, Fig. 6 (A) shows the first movement and Fig. 6 (B) shows the second movement;

Fig. 7 is a view of a schematic configuration showing a configuration of a refrigerant circuit and the movement during the heating and humidifying operation according to the first embodiment, Fig. 7 (A) shows the first movement and Fig. 7 (B) shows the second movement;

Fig. 8 is a perspective view showing a schematic configuration of a heat exchanger according to the first embodiment;

Fig. 9 is an enlarged view of a main part of the heat exchanger showing the arrangement of corrugated sheet fins according to the first embodiment;

Fig. 10 is an enlarged view of a main part of a heat exchanger showing the arrangement of corrugated sheet fins according to an example of modification of the first embodiment;

Fig. 11 is a perspective view showing a schematic configuration of a heat exchanger according to a second embodiment;

Fig. 12 is an exploded perspective view showing a schematic configuration of the heat exchanger according to the second embodiment;

Fig. 13 is an enlarged sectional view of a main part of the heat exchanger according to the second embodiment, Fig. 13 (A) shows a state before assembly and Fig. 13 (B) shows a state after assembly;

Fig. 14 is an enlarged view of a main part of the heat exchanger showing the arrangement of the corrugated sheet fins and the flat sheet fins according to the second embodiment,

Fig. 15 is an enlarged sectional view showing a main part of a heat exchanger according to a first example of modification of the second embodiment, Fig. 15 (A) shows a state before assembly and Fig. 15 (B) shows a state after assembly;

Fig. 16 is an enlarged view of a main part of a heat exchanger showing the arrangement of corrugated sheet fins and flat sheet fins according to a second example of modification of the second embodiment ,

Fig. 17 is a perspective view showing a schematic configuration of a heat exchanger according to a third embodiment, Fig. 17 (A) shows a state before assembly and Fig. 17 (B) shows a state after assembly;

Fig. 18 is a perspective view showing a schematic configuration of a heat exchanger according to a first example of modification of the third embodiment, Fig. 18 (A) shows a state before assembly and Fig 18 (B) shows a state after assembly;

Fig. 19 is a front view and a side view of the corrugated sheet fins according to a first example of modification of other embodiments;

Fig. 20 is a schematic side view of the corrugated sheet fins according to a second example of modification of the other embodiments;

Fig. 21 is a schematic side view of the corrugated sheet fins according to the second example of modification of the other embodiments.

Description of the numeric references

10

Air conditioner

40

Refrigerant circuit (heating medium circuit)

55

Internal heat exchanger (temperature control part, heat control heat exchanger

temperature)

56

First adsorption heat exchanger (humidity control part)

57

Second adsorption heat exchanger (humidity control part)

5

10

fifteen

twenty

25

30

35

40

Four. Five

fifty

60

Heat exchanger

61

Heat transfer tube

65

Flat blade fin

66

Hole

67

First collar

70

Corrugated Blade Fin

75

Hole

76

Second collar

78

Flat portion

Best way to carry out the invention

Embodiments of the present invention will be described in detail in relation to the figures.

First embodiment of the invention

A first embodiment of the present invention will be described. An air conditioner 10 of this embodiment carries out a steam compression refrigeration cycle by circulating the refrigerant within a refrigerant circuit 40 as a heating means circuit to process both the inner sensitive heat load and the latent heat load.

Air conditioner setup

As shown in Fig. 1, it shows an air conditioner of a type called separation and has an internal unit 11 and an external unit 12. The internal unit 11 includes an internal heat exchanger 55, a First adsorption heat exchanger 56 and a second adsorption heat exchanger 57 and is installed into the interior space. The internal unit 11 is of a type called wall mounting and is fixed to an internal wall surface. On the other hand, the external unit 12 includes an external heat exchanger 54 and is installed towards the outer space.

The internal unit 11 and the external unit 12 are connected to each other by a communication tube 43 on the gas side and a communication tube 44 on the liquid side. A compressor 50 and an external fan 14 in addition to the external heat exchanger 54 are housed inside an external housing 13 of the external unit 12.

The internal unit 11 has an internal housing 20 with an elongated horizontal box shape. The internal heat exchanger 55, the first adsorption heat exchanger 56 and the second adsorption heat exchanger 57 are arranged on the front surface of the internal housing 20. Specifically, the first adsorption heat exchanger 56 and the second adsorption heat exchanger 57 are arranged side by side on the upper portion of the front surface of the inner housing 20. When the inner housing 20 is seen from the front, the first adsorption heat exchanger 56 and the second exchanger Adsorption heat 57 are installed on the left side and on the right side. On the front surface of the internal housing 20, the internal heat exchanger 55, as a temperature control heat exchanger, is located below the first adsorption heat exchanger 56 and the second adsorption heat exchanger 57 and a air outlet 26 opens below the internal heat exchanger 55.

An internal space of the internal housing 20 is divided into a lateral space of the front surface and a lateral space of the rear surface. The lateral space of the rear surface of the internal housing 20 constitutes an escape passage 24. The lateral space of the frontal surface of the internal housing 20 is vertically partitioned. A lower space of the lateral space of the front surface is located on the side of the rear surface of the internal heat exchanger 55 and constitutes an air supply passage 23. On the other hand, an upper space of the lateral space of the front surface is horizontally partitioned. A left space located on the side of the rear surface of the first adsorption heat exchanger 56 constitutes a first space 21 and a right space located on the side of the rear surface of the second adsorption heat exchanger 57 constitutes a second space 22.

An aspirating fan 32 is housed inside the exhaust passage 24 of the internal housing 20. An exhaust duct 25 open towards the outer space is connected to the exhaust passage 24. On the other hand, an internal fan 31 is housed within the passage of air supply 23. The air supply passage 23 communicates with the air outlet 26.

The internal housing 20 is provided with four shock absorbers capable of opening 33 to 36. Specifically, a first air supply damper 33 is disposed between the first space 21 and the air supply passage 23. A first exhaust damper 34 is disposed between the first space 21 and the exhaust passage 24. A second air supply damper 35 is disposed between the second space 22 and the air supply passage 23. A second exhaust damper 36 is disposed between the second space 22 and the escape step

24.

As shown in Fig. 6 and Fig. 7, the compressor 50, an electric expansion valve 53 and two four-way switching valves 51, 52 are disposed within the refrigerant circuit 40. The heat exchanger external heat 54, the internal heat exchanger 55 and the two adsorption heat exchangers 56, 57 are likewise arranged within the refrigerant circuit 40.

The configuration of the refrigerant circuit 40 will now be described. The compressor 50 is connected to a first orifice of the first four-step switching valve 51 located on the discharge side thereof and is connected to a second orifice of the first valve four-step switching 51 located on the suction side of the latter. One end of the external heat exchanger 54 is connected to a third orifice of the first four-step switching valve 51 and the other end of the external heat exchanger 54 is connected to the first orifice of the first four-step switching valve 52. One end of the internal heat exchanger 55 is connected to a fourth orifice of the first four-step switching valve 51 and the other end of the internal heat switch 55 is connected to the second orifice of the second four-step switching valve 52. Within the refrigerant circuit 40, the first adsorption heat exchanger 56, the electric expansion valve 53 and the second adsorption heat exchanger 57 are arranged, in this order, from the third orifice to the fourth orifice of the second valve four-step switching 52.

A zone of the refrigerant circuit 40, where the compressor 50, the first four-step switching valve 51 and the external heat exchanger 54 are arranged, constitutes an external circuit 41 and is housed inside the external unit 12. On the other hand , a zone of the refrigerant circuit 40, in which the internal heat exchanger 55, the first and second adsorption heat exchangers 56, 57, the electric expansion valve 53 and the second four-step switching valve 52 are arranged , constitutes an internal circuit 42 and is housed inside the internal unit 11. An end of the internal circuit 42 located on the side of the second four-step switching valve 52 is connected to one end of the external circuit 41 on the side of the exchanger of external heat 54 by means of the communication tube 44 on the liquid side. One end of the internal circuit 42 located on the side of the external heat exchanger 55 is connected to one end of the external circuit 41 on the side of the first four-step switching valve 51 by means of the communication tube 43 on the gas side.

The external heat exchanger 54, the internal heat exchanger 55 and the adsorption heat exchangers 56, 57 are each a transverse fin type fin and the tube heat exchanger constituted by a heat transfer tube 61 and a multiplicity of fins. The internal heat exchanger 55 and the first and second adsorption heat exchangers 56, 57 are each constituted by a heat exchanger 60 in accordance with the present invention.

Within each of the heat adsorption exchangers 56, 57, an adsorption layer made of adsorbent is formed on the surface of each fin. Ceolite, silica gel, or similar substances can be used as adsorbent. Within each of the adsorption heat exchangers 56, 57 in which the adsorption layer is formed on the surface of each fin, moisture is transferred between the air passing between the fins and the adsorption layer. Each of the heat exchangers 56, 57 constitutes a humidity control part for adjusting the water content of the air to process the internal latent heat load.

In the external heat exchanger 54 and in the internal heat exchanger 55, no adsorbent is disposed on the surface of each fin and only heat exchange between the air and the refrigerant is carried out. The internal heat exchanger 54 exchanges heat between the external air and the refrigerant. The internal heat exchanger 55 exchanges heat between the internal air and the refrigerant. The heat exchanger 55 constitutes a temperature control part for adjusting the air temperature to process the internal sensitive heat load.

The first four-step switching valve 51 is switched between a first state in which the first orifice and the third orifice are connected to each other and the third orifice and the fourth orifice are interconnected (state shown in Fig. 6) and a second state in which the first hole and the fourth hole are connected to each other and the second hole and the third hole are connected to each other (state shown in Fig. 7). On the other hand, the second four-step switching valve 52 is switched between the first state in which the first orifice and the third orifice are connected to each other and the third orifice and the fourth orifice are interconnected (state shown in the Fig. 6 (A) and in Fig. 7 (B)) and the second state in which the first hole and the fourth hole are communicated with each other and the second hole and the third hole are communicated with each other (state shown in Fig. 6 (B) and in Fig. 7 (A)).

Heat exchanger configuration

As described above, the internal heat exchanger 55, the first adsorption heat exchanger 56 and the second adsorption heat exchanger 57 are each constituted by the heat exchanger 60 in accordance with the present invention. . Hereinafter, heat exchanger 60 will be described with reference to Fig. 8 and Fig. 9.

As shown in Fig. 8, the heat exchanger 60 incorporates a plurality of straight heat transfer tubes 61 and fins of the corrugated sheet type 70. The heat exchanger 60 is formed, as a whole, as a thick plate or as a flat rectangular parallelepiped. In heat exchanger 60, air passes from the front surface to the rear surface.

In the heat exchanger 60, the heat transfer tubes 61 are arranged in an almost horizontal position at regular intervals. In the heat exchanger 60, the ends of the adjacent heat transfer tubes 61 are connected to each other with a U-shaped tube, not shown, to constitute one or more paths.

On the other hand, the corrugated sheet fins 70 are arranged in the axial direction of the heat transfer tubes 61 in regular steps, so that the surfaces of the fins can be orthogonal with respect to the axial direction of the tubes of heat transfer 61. Each corrugated sheet fin 70 is shaped like a corrugated sheet in which the ridges 71 and depressions 72 are alternately shaped in a constant cycle. That is, the waveform of the corrugated sheet fin 70 is a triangular wave and the peaks 71 and the depressions 72 are alternately constituted in a constant cycle in the vertical direction in Fig.

8. Here, a projection portion toward the side near the right is defined as the crest 71 and a projection portion toward the rear side on the left is defined as the depression 72 in this figure.

In each of the corrugated sheet fins 70, a lateral surface located on the upstream side of the air flow is defined as a front edge 73 and a lateral surface located on the downstream side of the air flow is defined as an edge rear 74. That is, on the corrugated sheet fins 70, the front edges 73 are located on the side of the front surface of the heat exchanger 60 and the rear edges 74 are located on the side of the rear surface of the heat exchanger 60

Passages 75 for insertion of heat transfer tubes 61 through them all are constituted on corrugated sheet fins 70. Cylindrical collars 76, which are located in continuity with the peripheries of the passage holes 75, are arranged in projection on the corrugated sheet fins 70. In Fig. 8, the collars 76 protrude from the surfaces of the corrugated sheet fins 70 towards the side near the right. The heat transfer tubes 61 are inserted into the collars 76, respectively, and the inner circumferential surfaces of the collars 76 are in intimate contact with the outer circumferential surfaces of the heat transfer tubes 61. The protruding ends of the Collars 76 are placed in contact with the adjacent corrugated sheet fin 70, thereby maintaining a distance between the corrugated sheet fins 70.

In the heat exchanger 60 configured in the manner indicated, a direction of the amplitude of the waveform of the corrugated sheet fins 70 is substantially parallel to the axial direction of the heat transfer tube 61. A direction of the line of Crest of the waveform of the corrugated sheet fins 70 is orthogonal with respect to the side edges 73 and with respect to the rear edges 74 of the corrugated sheet fins 70.

In the heat exchanger 60, as shown in Fig. 9, the waveform cycle is identical along all adjacent corrugated sheet fins 70. In the heat exchanger 60, an amplitude W of the waveform of the corrugated sheet fin 70 is equal to one passage, FP, between the corrugated sheet fins 70. In the heat exchanger 60, the air passing between the corrugated sheet fins 70 arranged in steps Regular exchanges heat with the refrigerant flowing through the heat transfer tubes 61 arranged to pass through the corrugated sheet fins 70.

Within the heat exchangers 60 used as the first and second adsorption heat exchangers 56, 57 the adsorption layers are constituted on the surfaces of the corrugated sheet fins

70. Within the heat exchangers 60 used as the first and second adsorption heat exchangers 56, 57, the air that passes between the corrugated sheet fins 70 arranged in regular steps exchanges heat with the refrigerant flowing through the Heat transfer tubes 61 arranged to pass through the corrugated sheet fins 70 and in contact with the adsorption layers formed on the surfaces of the corrugated sheet fins 70.

On the other hand, in the heat exchanger 60 used as the internal heat exchanger 55, no adsorption layer is formed on the surfaces of corrugated sheet fins 70. Inside the heat exchanger 60 used as the internal heat exchanger 55 , the air passing between the corrugated sheet fins 70 arranged in regular passages exchanges heat with the refrigerant flowing through the heat transfer tubes 61 arranged to pass through the corrugated sheet fins 70.

Operational behavior

The air conditioner 10 in this embodiment performs a cooling and dehumidification operation and a heating and humidifying operation.

Within the air conditioner 10, when the internal fan 31 and the aspirating fan 32 are actuated, the internal air flows inside each of the elements consisting of the internal heat exchanger 55, the first adsorption heat exchanger 56 and the second adsorption heat exchanger 57. When the fan 14 is operated, the external air flows to the interior of the external heat exchanger 54.

Cooling and dehumidification operation

Next, with reference to Fig. 2, Fig. 3 and Fig. 6, the movements of the cooling and dehumidification operation will be described.

As shown in Fig. 6, in the refrigerant circuit 40, the first four-step switching valve 51 is set in the first state, the opening degree of the electric expansion valve 53 is properly adjusted, the External heat exchanger 54 serves as a condenser and the internal heat exchanger 55 serves as an evaporator. Then, as shown in Fig. 2 and Fig. 3, the internal air cooled by the internal heat exchanger 55 passes through the air supply passage 23 and is sent back into the interior space through the air outlet 26, while the external air, which absorbs the heat from the refrigerant of the external heat exchanger 54 is discharged into the outer space.

During the cooling and dehumidification operation, a first movement is repeated alternately, in which the first adsorption heat exchanger 56 serves as a condenser and the second adsorption heat exchanger 57 serves as an evaporator and a second movement, in that the second adsorption heat exchanger 57 serves as a condenser and the first adsorption heat exchanger 56 serves as an evaporator.

In the first movement, a regeneration movement of the first adsorption heat exchanger 56 and an adsorption movement of the second adsorption heat exchanger 57 are developed in parallel. As shown in Fig. 6 (A), during the first movement, the second four-step switching valve 52 is set in the first state. The refrigerant discharged from the compressor 50 is condensed during its passage through the external heat exchanger 54 and by the first adsorption heat exchanger 56, in this order, and is decompressed by the electric expansion valve 53. Next, the refrigerant is evaporated during its passage through the second adsorption heat exchanger 57 and by the internal heat exchanger 55, in this order, sucked into the compressor 50 and compressed. In the first movement, the high pressure refrigerant, as a heating means for heating, is supplied to the first adsorption heat exchanger 56 and the low pressure refrigerant, as a heating means for cooling, is supplied to the second heat exchanger of adsorption 57.

In the first movement, as shown in Fig. 2, the first exhaust damper 34, and the second supply air damper 35 are arranged in the open state and the first air supply damper 33 and the second damper Air exhaust 36 are placed in closed state. In the first adsorption heat exchanger 56, the moisture is desorbed by an adsorbent heated by the refrigerant and the adsorbed moisture is emitted into the air. Together with the internal air, the desorbed moisture of the first adsorption heat exchanger 56 flows through the interior of the exhaust passage 24 from the first space 21 through the first exhaust damper 34 and is discharged into the outer space through the duct Exhaust 25. Within the second adsorption heat exchanger 57, the internal air humidity is adsorbed by the adsorbent, the internal air is dehumidified and the adsorption heat generated at this time is absorbed by the refrigerant. The internal air dehumidified by the second adsorption heat exchanger 57 flows through the interior of the air supply passage 23 from the second space 22 through the second air supply damper 35 and is returned to the outer space through the outlet of air 26.

In the second movement, the adsorption movement of the first adsorption heat exchanger 56 and the regeneration movement of the second adsorption heat exchanger 57 are carried out in parallel. In the second movement, as shown in Fig. 6 (B), the second four-step switching valve 52 is set in the second state. In this state, the refrigerant discharged from the compressor 50 is condensed during its passage through the external heat exchanger 54 and the second adsorption heat exchanger 57, in this order, and is decompressed by the electric expansion valve 53. A Then, the refrigerant is evaporated during its passage through the first adsorption heat exchanger 56 and the internal heat exchanger 55, in this order, sucked into the compressor 50 and compressed. In the second movement, the high pressure refrigerant, as a heating means for heating, is supplied to the second adsorption heat exchanger 57 and the low pressure refrigerant, as a heating means for heating, is supplied to the first heat exchanger of adsorption 56.

In the second movement, as shown in Fig. 3, the first air supply damper 33 and the second exhaust damper 36 are placed in the open state and the first exhaust damper 34 and the second exhaust damper 35 They are located in a closed state. In the first adsorption heat exchanger 56, the humidity of the internal air is adsorbed by the adsorbent, the internal air is dehumidified and the heat of adsorption generated at this time is adsorbed by the refrigerant. The dehumidified internal air in the first adsorption heat exchanger 56 flows into the air supply passage 23 from the first space 21 through the first air supply damper 33 and is sent back into the interior space through of the air outlet 26. In the second adsorption heat exchanger 57, the moisture is desorbed by adsorbent heated by the refrigerant and the desorbed moisture is expelled into the air. Together with the internal air, the desorbed moisture of the second adsorption heat exchanger 57 flows into the exhaust passage 24 from the second space 22 through the second exhaust damper 36 and is discharged into the outer space through the duct exhaust 25.

Here, in a general air conditioner without adsorption heat exchangers 56, 57, the evaporation temperature of the refrigerant in the internal heat exchanger during the cooling operation is set as a value lower than the dew point temperature of the internal air (for example, approximately 5 ° C. This is carried out in order to dehumidify the incoming air by condensing the humidity of the incoming air by means of the internal heat exchanger.

In contrast, during the cooling and dehumidification operation of the air conditioner 10 in this embodiment, since the internal air is dehumidified by the adsorption heat exchangers 56, 57, the internal air does not need to be dehumidified by the heat exchanger. internal heat 55. In this way, in the air exchanger 10, the evaporation temperature of the refrigerant in the internal heat exchanger 55 during the cooling and dehumidification operation is set as a higher value than that of a general air conditioner . Specifically, the evaporation temperature of the refrigerant in the internal heat exchanger 55 during the cooling and dehumidification operation is set to be higher than the dew point temperature of the air passing through the internal heat exchanger 55 For this reason, no type of drainage water is generated in the internal heat exchanger 55 even during the cooling and dehumidification operation.

During the cooling and dehumidifying operation of the air conditioner 10, in this embodiment, in the first movement, the second adsorption heat exchanger 57 serves as an evaporator, and in the second movement, the first adsorption heat exchanger 56 It serves as an evaporator. In adsorption heat exchangers 56, 57 used as evaporators, the humidity of the internal air passing between the corrugated sheet fins 70 is absorbed by the adsorption layer, the adsorption heat generated at this time is adsorbed and the refrigerant of the heat transfer tubes 61 is evaporated. That is, in the adsorption heat exchangers 56, 57 used as evaporators is not markedly reduced, while the absolute humidity of the internal air passing through the adsorption heat exchangers is reduced. For this reason, water condensation is hardly generated on the surfaces of the corrugated sheet fins 70 of the adsorption heat exchangers 56, 57 used as evaporators.

Heating and humidification operation

Next, with reference to Fig. 4, Fig. 5 and Fig. 7, the movements of the heating and humidifying operation will be described.

As shown in Fig. 7, in the refrigerant circuit 40, the first four-step switching valve 51 is set in the second state, the opening degree of the electric expansion valve 53 is properly adjusted , the internal heat exchanger 55 serves as a condenser, and the external heat exchanger 54 serves as an evaporator. Next, as shown in Fig. 4 and Fig. 5, the internal air heated by the internal heat exchanger 55 passes through the air supply passage 23 and is sent back into the interior space through the air outlet 26, while the external air, which discharges heat on the refrigerant in the external heat exchanger 54, is discharged into the outer space.

During the heating and humidifying operation, a first movement, in which the first adsorption heat exchanger 56 serves as a condenser and the second adsorption exchanger 57 serves as an evaporator, and a second movement, in which the second heat exchanger of adsorption 57 serves as a condenser and the first adsorption exchanger 56 serves as an evaporator, they are repeated alternately.

In the first movement, the adsorption movement of the first adsorption heat movement 56 and the regeneration movement of the second adsorption heat exchanger 57 are carried out in parallel. In the first movement, as shown in Fig. 7 (A), the second four-step switching valve 52 is set in the second state. In this state, the refrigerant discharged from the compressor 50 is condensed during its passage through the internal heat exchanger 55 and the first adsorption heat exchanger 56, in this order, and decompressed by the electric expansion valve 53. Next , the refrigerant is evaporated during its passage through the second heat exchanger 57 and the external heat exchanger 54 in this order, aspirate into the compressor 50 and compressed. In the first movement, the high pressure refrigerant, as a heating means for heating, is supplied to the first adsorption heat exchanger 56 and the low pressure refrigerant, as a heating means for cooling, is supplied to the second heat exchanger of adsorption 57.

In the first movement, as shown in Fig. 4, the first air supply damper 33 and the second exhaust damper 36 are placed in the open state and the first exhaust damper 34 and the second air supply damper Air 35 are placed in closed state. In the first adsorption heat exchanger 56, the moisture is desorbed from an adsorbent heated by the refrigerant and the desorbed moisture is expelled into the air. Dehumidified internal air in the first adsorption heat exchanger 56 flows into the air supply passage 23 from the first space 21 through the first air supply damper 33 and is sent back to the interior space through the air outlet 26. In the second heat exchanger 57, the humidity of the internal air is adsorbed by the adsorbent, the internal air is dehumidified and the heat of adsorption generated at this time is adsorbed by the refrigerant. The internal air from which moisture is taken from the second Adsorption Heat Exchanger 57 flows through the interior of the exhaust passage 24 from the second space 22 through the second exhaust damper 36 and is discharged into the outer space through of the second exhaust duct 25.

In the second movement, the adsorption movement of the first adsorption heat exchanger 56 and the regeneration movement of the second adsorption heat buffer 57 are carried out in parallel. In the second movement, as shown in Fig. 7 (B), the second four-step switching valve 52 is set in the first state. In this state, the refrigerant discharged from the compressor 50 is condensed during its passage through the internal heat exchanger 55 and the second adsorption heat exchanger 57, in this order, and successively decompressed by the electric expansion valve 53. A Then, the refrigerant is evaporated during its passage through the first adsorption heat exchanger 56 and the internal heat exchanger 54, in this order, sucked into the compressor 50 and compressed. In the second movement, the high pressure refrigerant, as a heating means for heating, is supplied to the second heat exchanger 57 and the low pressure refrigerant, as a heating means for cooling, is supplied to the first adsorption heat exchanger 56 .

In the second movement, as shown in Fig. 5, the first exhaust damper 34 and the second air supply damper 35 are placed in the open state and the first air supply damper 33 and the second air damper Exhaust 36 are placed in closed state. In the first adsorption heat exchanger 56, the humidity of the internal air is adsorbed by the adsorbent, the internal air is dehumidified and the heat of adsorption generated at this time is adsorbed by the refrigerant. Dehumidified internal air in the first heat exchanger 56 flows into the exhaust passage 24 and from the first space 21 through the first air damper 34 and is discharged into the interior space through the exhaust duct 25. In the second adsorption heat exchanger 57, the moisture is desorbed from the adsorbent heated by the refrigerant and the desorbed moisture is transmitted to the internal air. The humidified internal air in the second adsorption heat exchanger 57 flows into the supply passage 23 from the second space 22 through the second air supply damper 35 and is sent back into the interior space through the air outlet 26.

During the heating and humidifying operation of the air conditioner 10, in this embodiment, in the first movement, the second adsorption heat exchanger 57 serves as an evaporator and in the second movement, the first adsorption heat exchanger 56 serves as evaporator Likewise, during the heating and humidifying operation, within the adsorption heat exchangers 56, 57 used as evaporators, the humidity of the internal air that passes through the corrugated sheet fins 70 is absorbed by the adsorption heat, the heat of adsorption generated at this time is absorbed and the refrigerant in the heat transfer tubes 61 is evaporated. Thus, similar to the cooling and dehumidification operation, during the cooling and dehumidification operation, water condensation is hardly generated on the surfaces of the corrugated sheet fins 70 of the adsorption heat exchangers 56 , 57 used as evaporators.

Effects of the first embodiment

In this embodiment, the heat exchanger 60 incorporating the corrugated sheet fin 70 is adopted as the internal heat exchanger 55 and as the adsorption heat exchangers 56, 57. Since the heat exchanger 60 employs the fins corrugated sheet 70, each of which has a surface area greater than a surface area of a flat sheet fin, a heat transfer area with the air in the heat exchanger 60 can be extended without causing the passage between the fins is smaller. In the heat exchanger 60 the corrugated sheet fins 70 are arranged such that the direction of the crest line of the waveform of the corrugated sheet fins 70 can be orthogonal with respect to the front surface and the back surface of the heat exchanger 60. For this reason, the flow of air passing through the heat exchanger 60 is not obstructed by the fins of corrugated sheet 70 and, therefore, the air passes unhindered from the front surface to the surface rear of the heat exchanger 60. Accordingly, by adopting the heat exchanger 60 as an internal heat exchanger 55 and the adsorption heat exchangers 56, 57, the heat transfer area on the air side can be extended while suppressing an increase in ventilation resistance in internal heat exchanger 55 and adsorption heat exchangers 56, 57, and The internal heat exchanger 55 and the adsorption heat exchangers 56, 57 can be considerably reduced in size.

Here, in the heat exchanger 60, when the humidity of the air is condensed on the fins of corrugated sheet 70, it cannot be said that there is no possibility that the condensed water generated (drainage water) has difficulties to flow. On the contrary, in the air conditioner 10, in this embodiment, even within any exchanger, between the heat exchanger 55 and the adsorption heat exchanger 56, 57, which are used as evaporator, the humidity of the air it hardly condenses or does not condense at all on the surfaces of the corrugated sheet fins 70. In this way the heat exchanger 60 incorporating the corrugated sheet fins 70 is extremely suitable as an internal heat exchanger 55 and as adsorption heat exchangers 56, 57 of the air conditioner 10 and, by adopting the heat exchanger 60, the internal unit 11 can be reduced in size.

Example of modification of the first embodiment

In the heat exchanger 60 adopted as an internal heat exchanger 55 and as adsorption heat exchangers 56, 57 in this embodiment, the waveform cycle of adjacent corrugated sheet fins 70 need not be the same. For example, as shown in Fig. 10, the waveforms of adjacent corrugated sheet fins 70 can be displaced in half a cycle. In this case, in the heat exchanger 60, the peaks 71 and the depressions 72 of the adjacent corrugated sheet fins 70 are in contact with each other and the air passes through the space having a rectangular cross-section surrounded by the fins of adjacent corrugated sheet 70.

Second embodiment of the invention

A second embodiment of the invention will be described below. In this embodiment, in the air conditioner 10 of the first embodiment, the configuration of the heat exchanger 60 adopted as an internal heat exchanger 55 and as the adsorption heat exchangers 56 is modified,

57. At this time, the configuration of this heat exchanger 60 will be described.

As shown in Fig. 11 and Fig. 12, the heat exchanger 60 in this embodiment has a plurality of straight heat transfer tubes 61, of flaps of flat sheet 65 in the form of flat sheet and of corrugated sheet fins 70 in the form of corrugated sheet. The heat exchanger 60 is formed, as a whole, as a thick plate or as a thick plate as a flat rectangular parallelepiped. In heat exchanger 60, air passes from the front surface to the rear surface.

In the heat exchanger 60, the heat transfer tubes 61 are arranged horizontally at regular intervals. In the heat exchanger 60, the ends of the adjacent heat transfer tubes 61 are connected to each other with a U-shaped tube, not shown, to constitute one or more paths. The flat blade fins 65 and the corrugated sheet fins 70 are alternately arranged in constant steps in the axial direction of the heat transfer tube 61, so that the fin surfaces can be orthogonal with respect to the axial direction of heat transfer tube 61.

Each flat blade flap 65 is shaped as a vertically flat rectangular plate. Passages 66, for the insertion of the heat transfer tubes 61, are constituted by crossing said holes on the flaps of flat sheet 65. First cylindrical collars 67, arranged as continuity of the peripheries of the passage holes 66 are arranged in a slope on the flaps of flat sheet 65. In Fig. 11 and in Fig. 12, the first collars 67 protrude from the surfaces of the flaps of flat sheet 65 towards the side near the right.

Corrugated sheet fins 70 are configured as in the first embodiment, that is, each of the corrugated sheet fins 70 is configured as a corrugated sheet in which peaks 71 and depressions 72 are alternately constituted in a given cycle and the direction of the crest line of the waveform is orthogonal with respect to the front edges 73 and with respect to the rear edges 74 of the corrugated sheet fins 70. The passage holes 75 for insertion through them the heat transfer tubes 61 are formed on the corrugated sheet fins 70 and on the second cylindrical collars 76, which are arranged in continuity with the peripheries of the through holes 75 and protrude therefrom. In Fig. 11 and Fig. 12, the second collars 76 protrude from the surfaces of the corrugated sheet fins 70 towards the side near the right.

As shown in Fig. 13, in the heat exchanger 60, the first collars 67 of the flat blade fins 65 are inserted into the second collars 76 of the corrugated sheet fins 70 and the heat transfer tubes 61 are inserted into the first collars 67 of the flat blade fins 65. That is, in this heat exchanger 60, the heat transfer tubes 61 are inserted into the through holes 66, 75 of the blade fins flat 65 and on the corrugated sheet fins 70. In this heat exchanger 60, by extending the heat transfer tubes 61, the outer circumferential surfaces of the heat transfer tubes 61 are placed in intimate contact with the surfaces outer circumferential of the first collars 67 and the outer circumferential surfaces of the first collars 67 are placed in intimate contact with the circumferential surfaces it is internal to the second collars 76. Also, in this heat exchanger 60, as shown in Fig. 14, the waveform cycle of the corrugated sheet fins 70 is the same.

In the heat exchanger 60 used as the first and second adsorption heat exchangers 56, 57 the adsorption layers are constituted on the surfaces of the flat sheet fins 65 and the corrugated fin surfaces 70. In the heat exchanger 60 as adsorption heat exchangers 56, 57, the air that passes between the flat sheet fins 65 and the corrugated sheet fins 70, which are alternately arranged in constant steps, exchange heat with the refrigerant flowing through the heat transfer tubes 61 arranged to pass through the flat sheet fins 65 and through the corrugated sheet fin 70 and at the same time be in contact with the adsorption layers constituted on the fin surfaces of flat blade 65 and corrugated blade flap 70.

On the other hand, in the heat exchanger 60 used as an internal heat exchanger 55 no adsorption layer is constituted on the surfaces of the flat sheet fin 65 and on the corrugated sheet fin

70. In the heat exchanger 60 used as an internal heat exchanger 55, the air passing between the flat blade fins 65 and the corrugated sheet fins 70, which are alternately arranged in constant steps, exchange heat with the refrigerant flowing through the heat transfer tubes 61 arranged to pass through the flat sheet fins 65 and through the corrugated sheet fin 70.

In this embodiment, the same effects as those obtained in the first embodiment can be obtained.

First example of modification of the second embodiment

The following configuration of the heat exchanger 60 can be adopted in this embodiment. In the following lines, a heat exchanger 60 will be described in an example of modification with reference to Fig.

fifteen.

In this heat exchanger 60, the protrusion direction of the first collars 67 located on the flat blade fins 65 is opposite the protrusion direction of the second collars 76 located on the corrugated foil fins 70. In this heat exchanger 60, the second collars 76 of the corrugated sheet fins 70 are inserted into the first collars 67 of the flat sheet fins 65 and the heat transfer tubes 61 are inserted into the second collars 76 of the corrugated sheet fins

70. That is, in the heat exchanger 60, the heat transfer tubes 61 are inserted into the through holes 66, 75 of the flat sheet fins 65 and the corrugated sheet fins 70. In the heat exchanger 60, by extending the heat transfer tubes 61, the outer circumferential surfaces of the heat transfer tubes 61 are placed in intimate contact with the inner circumferential surfaces of the second collars 76 and the outer circumferential surfaces of the second collars 76 are in contact with the inner circumferential surfaces of the second collars 67.

Second example of modification of the second embodiment

In the heat exchanger 60 in this embodiment, the waveform cycle of adjacent corrugated sheet fins 70 need not be the same. For example, as shown in Fig. 16, the waveforms of a pair of adjacent corrugated sheet fins 70 through the flat sheet fin 65 can be displaced in half a cycle.

Third example of modification of the second embodiment

In this embodiment, in the heat exchanger 60 which constitutes the adsorption heat exchangers 56, 57, the adsorption layer may be constituted only on the surfaces of the corrugated sheet fins 70, conversely, only on the flat blade fin surfaces 65.

Third embodiment of the invention

A third embodiment of the present invention will be described below. In this embodiment, the air conditioner 10 of the second embodiment modifies the configuration of the heat exchanger 60 used as the internal heat exchanger 55 and as the adsorption heat exchangers 56,

57. The differences between this embodiment and the second embodiment in the configuration of the heat exchanger 60 will be described below.

As shown in Fig. 17, this embodiment is different from the second embodiment in the configuration of the corrugated sheet fins 70 of the heat exchanger 60. Specifically, on the corrugated sheet fins 70 In this embodiment, a plurality of notches 77 are formed and no second collar 76 is incorporated. The notch 77 is formed by cutting a portion of the corrugated sheet fin 70 at a predetermined width from the rear edge side 74 towards the side of the front edge 73. The width of the notch 77 is almost the same or greater than the outer diameter of the first collar 67 of the flat blade fin 65. The passage of the notches 77 on the corrugated sheet fin 70 it is equal to the passage of the first collars 67 on the flat blade fin 65.

In the heat exchanger 60, in this embodiment, by inserting the heat transfer tubes 61 into the first collars 67 of the flat sheet fins 65 and by extending the heat transfer tubes 61, the outer circumferential surfaces of the heat pipes 61 are placed in contact with the inner circumferential surfaces of the first collars 67. The corrugated sheet fin 70 is inserted between the flat sheet fins 65 fixed to the heat transfer tubes 61 to that is held between the flaps of flat sheet 65 located on both sides of these. Thus, in the heat exchanger 60 of this embodiment, the corrugated sheet fin 70 is inserted between two adjacent flat sheet fins 65 to be held between the flat sheet fins 65 located on both sides thereof.

In the event that the adsorption heat exchangers 56, 57 are constituted by this heat exchanger 60, the adsorption layers are formed on the surfaces of the flat sheet fins 65 and the surfaces of the corrugated sheet fins 70. In the event that the internal heat exchanger 55 is constituted by this heat exchanger 60, no adsorption layer is constituted on the surface of the flat sheet fins 65 and on the surfaces of the corrugated sheet fins 70. These points are the same as in the second embodiment. In this embodiment, the same effects as those in the first embodiment and those in the second embodiment can be obtained.

First example of modification of the third embodiment

The following configuration of heat exchanger 60 can be adopted in this embodiment. In the following lines, a heat exchanger 60 of this modification example will be described, with reference to Fig. 18.

In the heat exchanger 60 of this modification example, two corrugated sheet fins 70 are inserted between a pair of flat sheet fins 65 arranged in constant steps. A width LW of the corrugated sheet fin 70 is smaller than a width of the flat sheet fin 65. Specifically, the width LW of the corrugated sheet fin 70 is equal to a width LF between the first collar 67 and the front edge 73 of the flat blade flap 65. In the flat blade flap 65, a width between the first collar 67 and the rear edge 74 is likewise the width LF. In the heat exchanger 60, the corrugated sheet fins 70 are held between the flat sheet fins 65 located on the two sides thereof.

Second example of modification of the third embodiment

In this embodiment, in the heat exchanger 60 which constitutes the adsorption heat exchangers 56, 57, the adsorption layer may be constituted only on the corrugated sheet fins 70 or vice versa, only on the fin surfaces. flat blade 65.

Other embodiments

First example of modification

In each of the aforementioned embodiments, the flat portions 78 may be constituted on the corrugated sheet fins 70 of the heat exchanger 60. As shown in Fig. 19, a relatively narrow flat portion 78 is formed on a portion along the leading edge 73 and on a portion along the trailing edge 74 on each of the corrugated fins 70 in the modification example. When the flat portions 78 are formed on the corrugated sheet fins 70, the stiffness of the corrugated sheet fins 70 is ensured and the corrugated sheet fins 70 are prevented from deforming in the orthogonal direction with respect to the fin surfaces . In the corrugated sheet fins 70, the flat portion 78 may be disposed only on the portion along the leading edge 73 or only on the portion along the trailing edge 74.

Second example of modification

In each of the above-mentioned embodiments, although the waveform of the corrugated sheet fins 70 of the heat exchanger 60 is shaped as a triangular wave, the waveform of the corrugated sheet fins 70 is not limited to the triangular wave

For example, as shown in Fig. 20, the waveforms of the corrugated sheet fins 70 may be a curved surface wave, in which a convex arc and a concave arc are repeated alternately. Even when the waveform of the corrugated sheet fins 70 is the wave of the curved surface, the waveform of the corrugated sheet fins 70 is not limited to the curved surface wave in which the surfaces are repeated and may Be a sine wave. When the waveform of the corrugated sheet fins 70 is the curved surface wave, a cross section of the space defined by the corrugated sheet fins 70 approaches a circle and, in this way, the pressure loss can be suppressed of the air that passes through space.

As shown in Fig. 21, the waveform of the corrugated sheet fins 70 may be a rectangular wave in which an convex trapezoid and a concave trapezoid are repeated alternately. Since the waveform of the corrugated sheet fins 70 is the rectangular wave, in the heat exchanger 60 incorporating only the corrugated sheet fins 70 of the first embodiment, the contact area between the adjacent corrugated sheet fins 70 is increased, thereby increasing the amount of heat transferred between adjacent corrugated sheet fins 70. In this case, in the heat exchanger 60 incorporating corrugated sheet fins 70 and flat sheet fins 65 of the second form In the embodiment, the contact area between the adjacent corrugated sheet fin 70 and the flat sheet fin 65 is increased, thereby increasing the amount of heat transferred between adjacent corrugated sheet fins 70 and the flat sheet fins 65. Accordingly, in this case, the temperature of the fins arranged in the heat exchanger 60 can be averaged and, thus, can be efficiency improved thereby improving the performance of the heat exchanger 60.

Third example of modification

In each of the above-mentioned embodiments, on the corrugated sheet fins 70 of the heat exchanger 60, the direction of the crest line of the waveform is orthogonal with respect to the front edges 73 and with respect to the edges rear 74 of the corrugated sheet fins 70. However, the angle that forms the direction of the crest line of the waveform with the front edges 73 and with the rear edges 74 of the corrugated sheet fins 70 is not necessary That is exactly 90 degrees. In each of the above-mentioned embodiments, the direction of the crest line of the waveform of the corrugated sheet fins 70 is arranged to be substantially orthogonal with respect to the front edges 73 and with respect to the rear edges 74 so that the flow of air passing from the front surface to the rear surface of the heat exchanger may not be obstructed by the corrugated sheet fins

70. Accordingly, if the flow of air passing through the heat exchanger is obstructed, even when the angle that forms the direction of the crest line of the corrugated sheet fins 70 with the front edges 73 and with the rear edges 74 shifts slightly from the exact 90 degrees (for example, even when the angle shifts from the exact 90 degrees by ± 5 degrees), it can be said that the direction of the crest line of the waveform is substantially orthogonal with respect to the front edges 73 and with respect to the rear edges 74.

Fourth example of modification

In each of the above-mentioned embodiments, the humidity control parts are constituted by two adsorption heat exchangers 56, 57. However, the humidity control parts only need to adjust the humidity of the air by the use of the adsorbent and, in this way, are not limited to the adsorption heat exchangers 56, 57. For example, the humidity control part may be constituted by an adsorption rotor used in general rotor dehumidifiers. The adsorption rotor is provided with a honeycomb-like disc material and one per adsorption layer formed on the surface of the base material. When the air is sent directly to the adsorption rotor, the humidity of the air is adsorbed by the adsorption layer while the air passes through the adsorption rotor thus dehumidifying the air. When the air heated by a heater or similar device is sent to the adsorption rotor, the moisture is desorbed by the adsorption layer heated by the air passing through the adsorption rotor and the desorbed moisture is expelled into the air.

Industrial applicability

As described hereinbefore, the present invention is effective in a heat exchanger for exchanging heat between a fluid, such as a refrigerant, and air and in an air conditioner incorporating the heat exchanger. .

Claims (9)

1. A heat exchanger comprising a heat transfer tube (61) and a plurality of fins arranged in axial direction with respect to said heat transfer tube (61) and configured to exchange heat between a fluid flowing through of the heat transfer tube (61) and the air flowing between the fins, being arranged, to constitute the fins, a plurality of flat sheet fins (65) each of which is in the form of a flat sheet and a plurality of corrugated sheet fins (70) each of which is in the form of a corrugated sheet, the flat blade fins (65) and the corrugated sheet fins (70) are alternately arranged in the axial direction of the heat transfer tube (61), and a direction of the amplitude of the waveform of the corrugated sheet fins (70) is substantially parallel to an axial direction of the heat transfer tube (61), and a crest line direction of the waveform of The corrugated sheet fins (70) is substantially orthogonal with respect to a front surface and a rear surface of the heat exchanger so that it corresponds to an air passage direction characterized because the flat blade fins (65) and the corrugated sheet fins (70) have through holes (66, 75) for insertion through them of the heat transfer tubes (61), in which First cylindrical collars (67), which are arranged in continuity with the peripheries of the through holes (66), are arranged in projection on the flaps of flat sheet (65) and second cylindrical collars (76), which they are arranged in continuity with the peripheries of the through holes (75), are arranged in projection on the corrugated sheet fin (70), The first collars (67) are inserted into the second collars (76) thus placing the internal circumferential surfaces of the second collars (76) in intimate contact with the internal circumferential surfaces of the first collars (67), while that the heat transfer tubes (61) are inserted into the first collars (67), thereby placing the inner circumferential surfaces of the first collars (67) in intimate contact with the outer circumferential surfaces of the tubes heat transfer (61). 2. A heat exchanger comprising a heat transfer tube (61) and a plurality of fins arranged in axial direction with respect to the heat transfer tube (61) and configured to exchange heat between a fluid flowing through the tube and heat transfer (61) and the air flowing between the fins, being arranged, to constitute the fins, of a plurality of flat sheet fins (65) each of which has the form of a flat sheet and a plurality of corrugated sheet fins (70) each of which has the form of a corrugated fin, the flat blade fins (65) and the corrugated sheet fins (70) are alternately arranged in the axial direction relative to the heat transfer tube (61), and a direction of the amplitude of the waveform of the corrugated sheet fins (70) is substantially parallel to an axial direction of the heat transfer tube (61), and a crest line direction of the waveform of The corrugated sheet fins (70) are substantially orthogonal with respect to the front surface and to a rear surface of the heat exchanger so that it corresponds to an air passage direction characterized because the flat blade fins (65) and the corrugated sheet fins (70) have through holes (66, 75) for insertion through them of the heat transfer tubes (61), in which First cylindrical collars (67), which are arranged in continuity with the peripheries of the through holes (66) are arranged in projection on the flaps of flat sheet (65) and second cylindrical collars (76), which are disposed in continuity with the peripheries of the through holes (75), are arranged in projection on the fins of corrugated sheet (70), the second collars (76) are inserted into the first collars (67), thereby placing the outer circumferential surfaces of the second collars (76) in intimate contact with the inner circumferential surfaces of the first collars (67), while the heat transfer tubes (61) are inserted into the second collars (76), thereby placing the inner circumferential surfaces of the second collars (76) in intimate contact with the inner circumferential surfaces of the tubes heat transfer (61). 3. The heat exchanger according to claims 1 or 2, wherein each corrugated sheet fin (70) is in contact with the flat sheet fins (65) located on both sides of the corrugated sheet fin (70). 4. The heat exchanger according to claims 1 or 2, wherein the flat portions (78) are formed along the sides of the corrugated sheet fins (70) that are orthogonal with respect to the direction of the crest line of the waveform of the latter. 5. The heat exchanger according to any one of claims 1 to 4, wherein, adsorption layers made of adsorbent are formed on the fins and moisture is transferred between the air passing between the fins and the adsorption layers. 6. The heat exchanger according to claim 5, wherein the adsorption layers made of adsorbent are formed on the surfaces of either flat sheet fins (65) or corrugated sheet fins (70), and moisture is transferred between the air that passes between the flaps of flat sheet (65) and the corrugated sheet fins (70) and the adsorption layers. 7. An air conditioner comprising a temperature control part (55) for the processing of the sensible heat load and humidity control parts (56, 57) for the processing of the latent heat load and carries out at least one cooling and dehumidification operation of the cooling air supplied to the outer space by means of the temperature control part (55) and the dehumidification of the air supplied to the interior space by the control parts (56, 57 ) of moisture, in which the humidity control parts (56, 57) control the water content of the air by using an adsorbent that adsorbs the humidity of the air, the temperature control part (55) is constituted by a temperature control heat exchanger (55) having the distinctive characteristics of claims 1 or 2, which exchanges heat between the heating means, for cooling, and the air of the cooling and dehumidification operation. 8. An air conditioner comprising a heat exchanger (60) having the distinctive features of claims 1 or 2 and a circuit (40) of a heating means for supplying a heating means, for cooling or a heating, to a heat transfer tube (61) of the heat exchanger (60), Alternately, it carries out a supply movement of the heating means, to cool the heat transfer tube (61) of the heat exchanger (60), thus enabling an adsorption layer of the heat exchanger ( 60) adsorbs the humidity of the air and a movement of supply of the heating medium, for heating, to the heat transfer tube (61) of the heat exchanger (60), thereby giving up the exorbitant moisture from the air adsorption layer of the heat exchanger (60), supplies to the interior space, either that of the air dehumidified by the heat exchanger (60) or the air humidified by the heat exchanger (60) and discharges into the outer space, either the dehumidified air by the heat exchanger (60), or by the air humidified by the heat exchanger (60), in which In the heat exchanger (60), the adsorption layers made of adsorbent are formed on fin surfaces and moisture is transferred between the air passing between the fins and the adsorption layers. 9. An air conditioner comprising a heat exchanger (60) having the distinctive features of claims 1 or 2 and a circuit (40) of a heating means for the supply of a heating means, for cooling or for heating, to a heat transfer tube (61) of the heat exchanger (60), Alternately, it carries out a movement of supply of the heating means, for cooling the heat transfer tube (61) of heat exchanger (60), thus enabling an adsorption layer of the heat exchanger (60) adsorbs the humidity of the air and a movement of supply of the heating medium, to achentate, to the heat transfer tube (61) of the heat exchanger (60), thus giving up to the air the desorbed moisture from the adsorption layer of the heat exchanger (60), supplies to the interior space, either the air dehumidified by the heat exchanger (60), either the air humidified by the heat exchanger (60), and discharges into the outer space either, the air dehumidified by the heat exchanger (60), either the air humidified by the heat exchanger (60), in which In the heat exchanger (60), the adsorption layers made of adsorbent are formed on the surfaces of either the flat sheet fins (65) or the corrugated sheet fins (70) and the moisture is transferred between the air passing between the flat sheet fins (65) and the corrugated sheet fins (70) and the adsorption layers.